Apparatus for supplying liquid fuel to internal-combustion engines



June 12, 1928.

W. B. S. WHALEY APPARATUS FOR SUPPLYING LIQUID FUEL TO INTERNAL COMBUSTION ENGINES Filed April 16, 1921 3 Sheets-Sheet William ZZVJM'I Z W /355g A TTORNE Y.

June 12, 1928.

W. B. S. WHALEY APPARATUS FOR SUPPLYING LIQUID FUEL TO INTERNAL COMBUSTION ENGINES s Sheets-Sheet 2 Filed April 16, 1921 fl'. f: 65 55 550 iiLyAfO.

'INVENTOR. llfillz'am 5 shril /z wliagfg y! A TTORNEY.

June 12, 1928.

'W."B. S. WHALEY APPARATUS FOR SUPPLYING LIQUID FUEL TO INTERNAL COMBUSTION ENGINES 3 Sheets-Sheet Filed April 16, 1921 vi il/1571" T 3 I f J M y. m m M N R W flfll. -A .Z V m 0 m A 0 0 W Q vvu. L 5 2 M W i MW M 2 q I J Z i w \J k U m u a m W V W Y g fl :M a A f M M MC w a W W W YD w PRESSURE PLUNGER PLUNGER Patented June 12, 1928.

UNITED STATES 1,673,277 PATENT OFFICE.

WILLIAM B. SMITH WHALEY, OF NEW YORK, N. Y., ASSIGNOR T0 WHALEY ENGINE PATENTS, INC., A CORPORATION OF DELAWARE.

APPARATUS FOR SUPPLYING LIQUID FUEL TO INTERNAL-COMBUSTION ENGINES.

Application filed April 16, 1921. Serial No. 462,053.

My invention relates to a liquid fuel injecting apparatus for internal combustion engines, and has for its object to provide an injecting apparatus which is regulably controlled to meet the different Working requirements of an engine and is designed to function on the principle of constant pressure of injection at any and all loads or speeds of the engine.

Another object of the invention is to provide a fuel injecting apparatus which is attended by mechamsms which render the same flexible and regulable and rovide an absolutely positive control there or to compel functioning thereof commensurate withthe specific working requirements of the engine and consistent with yielding in every case maximum economy and efliciency.

Another object of the invention is to pro vide a fuel injecting apparatus in which the oil is delivered at a nominally low pressure and raised therein to a relatively high pres-' sure to insure a steady, constant, and uniform flow throughout the discharging range of the apparatus for maintaining the principle of constant pressure of injection within the cylinder of the engine.

Another object of the invention is to provide a fuel injecting a paratus which receives fuel oil therem rom the supply at a low pressure and preheats it under high pressure preliminary to the discharging thereof for subsequently discharging the same from the apparatus as gas for commin-' gling and uniting with the oxidizing precompressed media of air in the combustion chamber of the engine for effecting combustion therein. 1

Another object of the invention is to provide the apparatus with an automatically operated discharge member which may be regulably adjusted to yield and function for discharging purposes at any desired predetermined pressure of the\oil within the apparatus.

Still another object of the invention is to provide a fuel oil injecting apparatus which may be coupled to operate in connection with a governing mechanism orvalve gear, and is adapted to automatically and variably function therewith in accordance with the different settings and actions thereof.

Other objects and advantages of the invention will be gathered from the description following herein and considered in connection with the accompanying drawing wherein the invention-is shown embodied.

The terms employed herein are used in the generic and descriptive sense to designate the elements illustrated, and are therefore not primarily intended as terms of limitation.

In order to illustrate the invention, I have shown in the accompanying three sheets of drawings an embodiment thereof wherein:

Fig. 1 represents a schematic art sectional and part elevational view 0 my apparatus coupled with an engine;

Fig. 1 represents a sectional view taken on line 11 on Fig. 1;

. Fig. 2 represents a plan view of Fig. 1;

Fig. 3 represents an enlarged view of the discharge valve of the apparatus (shown closed);

Fig. 3 represents a sectional view taken on line 3-3 on Fig. 3;

Fig. 4 represents a similar view to Fig. 3 but shows the open position of the discharge valve;

Fig. 5 represents a sectional on line 5--5 on Fig. 2;

Fig. 6 represents a similar view toFig. 5, showin part of same enlarged;

Fi represents a view showing the adjusta 1e cut-off plunger in open position;

Fig. 8 represents a sectional view taken i rbstantially on lines 8-8 and 8'8 on Fig. 9 represents a sectional view taken on line 9-9 on Fig. 8;

Fig. 10 represents a theoretical diagram showing the full range valve gear cycle of the apparatus;

Figs. 11 and 12. show part of the diagram shown in Fig. 10, but show two distinct cut-oil settings for the valve gear;

Figs. 13 to 15 inclusive represent diagrammatic, schematic views of the apparatus in action, showing the relative functioning features of the same in different settings or positions of the actuating valve gear mechamsm;

Fig. 16 represents a diagrammatic view showing the effective operating relations of the plungers of the within disclosed apparatus.

Like reference numerals or letters refer to like parts throughout the several views of the drawings.

view taken The numeral 25 (Fig. 1) represents an internal combustion engine cylinder head, which is preferably provided with the bore 26 within which is fitted the main valve casing 27 of the within apparatus and which communicates with the engine cylinder combustion chamber 28. Said valve casing is provided with a suitable flange 29 and is securely coupled with the cylinder head 25, as by means of the coupling bolts 30 which are spaced around said flange 29. The upper and exposed portion of said valve casing 27 is provided with the plunger housing 31 and the oil supply and cut-ofl' valve housing 32 which are angularly disposed, as shown in Fig. 2, and project from the main casing 27- The said casing 27 is further provided with the vertical bore 33 wl1ich incorporates the shoulder 34 at the bottom and the shoulder 35 at the top'thereof, as shown in Fig. 1; the horizontal and parallel displacement and pressure plunger bores 36 and 37 respectively, which are intercommunicatingly coupled by the cross-duct 38 (Fig. 8) and which duct is open through the channel 39 to the said vertical bore 33; the oil supply duct 40 which is coupled to-the oil supply pipe 41 communicating with the ball check valve bore 42, and which check valve bore 42 also communicates with said vertical bore 33 through the duct 44 provided therefor, as shown in the enlarged view in Fig- 6; and the cut-off valve bore 43, which is provided with the floatim diiferential cut-ofi' valve 45 designed with the nipple end 46 having the seat 47 provided with the vents 4-8.

49 represents a plug which threadedly en-. gages with the housing 32 for sealing the bore 43 and is provided with the opening 50 through which the adjusting spindle 51 of the spidered or vented spring adjusting member 52 is exposed, and which sprmg adjusting member is slidably fitted within the cut-off valve 45 to engage with the adjusting or load spring 53 positioned within the cutoff valve member 45 and serving to retain said cut-off member in the seated position, as shown in Fig. 6. The nipple end 46 of said cut-off valve 45 is thus exposed through the duct 54 to the ball check bore 42 which is preferably provided at the bottom thereof with the fitted sleeve 55. The latter abuts against the shoulder 56 provided therefor in the casing member and serves to provide an opening and valve seat 57 for the upper ball check 58 which is normally held seated thereagainst by the expansion spring 59 which may be adjustably set in relation thereto by the adjustable sealing plug 60 provided in the casing 32. Said sleeve 55 communicates with the duct 40 and is held secured in the bore 42 by the check 'valve plug 61 which abuts thereagainst and pro vides the valve opening and seat 62 which communicates with the duct 40, as shown in Fig. 6, and accommodates the lower ball check 63 which is spring-held to seat with said plug 61, as shown in said Fig. 6. 65 represents a vent opening which communicates with the inner end of the cut-off valve bore 43 and is connected by a suitable pipe 66 to the supply for draining back any air or oil which are preferably provided with the exposed forked ends 74 and 75 respectively and which ends are preferably designed to serve as crosshead guides within the crosshead bracket 76 which is rigidly secured to the casing 31, as shown in Figs. 1 and 8. The numeral 80 represents the discharge valve sleeve which is flanged at the top thereof to fit the shoulder 35 of the casing 27 and is provided at the bottom thereof with the threaded section 81 to which is fitted the removable valve seat collar 82 which seats against the shoulder 34 provided therefor in the casing 27, as shown in Fig. 3. valve sleeve member 80 is provided with the vertical opening 83 which is open to the bottom of said sleeve member 80. Said opening 83 registers with the duct 39 through the opening 84 and also registers with the duct 44 through the opening 85 (Figs. 1, 8 and 9). The valve seat collar 82 is preferably provided with the lower flange 86 which provides the annular oil well 87 surrounding the discharge or injecting valve seat 88 at the opening 89 of said valve seat collar- 90 represents the discharge or injecting alve plunger, which slidably fits within the valve sleeve 80. Said valve plunger s preferably hollowed out at the lower end and provided with the seat 91 which seats on the valve seat 88 provided therefor in the valve seat collar 82. Said valve plunger is also preferably shouldered at 92 to receive the diaphragm 93 and the spring collar 94 which are held firmly against the shoulder 92 by the nut 95 provided on the threaded section 96 at the upper end or stem section of said valve plunger. 97 represents a val re collar which is slidably fitted on the spring collar 94 and engages with the expansion spring 98 (Figs. 1 and 5). 100 represents the fixed valve stem bonnet which is securely bolted and coupled with the casing 27 to normally encase the associated valve stem parts and to clamp the diaphragm 93 be tween it and the casing member 27 and is externally threaded to accommodate the spring adjusting bonnet 101 and the check nut 102. The spring adjusting bonnet 101 engages with the valve collar 97 for adjusting the tension of the spring 98, and is preferably 7 provided with the adjustable limiting screw 103 at the top thereof which may be regu-' labl'y set to provide the desired space between it and the top of the valve stem 91 to limit the lift of the valve plunger 90 from its seat 88. The diaphragm 93 is made of suitable yielding'material, as for example copper, to functlon with the floating action of the valve plunger and to form a sealed joint for preventing leakage thereabout.

105 represents a rocker stud or shaft" crosshe'ad '7 4 'by'the'ilisplacement coiir'ictm'gi rod 110, andthepressure plunger arm being pivotally connected with the crosshead 75 by the'pressure plunger connecting rod 111 shown in Fig. 1. The pressure plunger or short arm 109 is preferably designed to yield both circumferential and radial adjustment, as indicated inFigs. 1 and 1, for regulabl positioning the point of engagement. he bracket 106 may be made integral with the casing member 27, as indi-' cated in Fig. 2, or separate therefrom and rigidly secured thereto or to any other convenient part of the engine in any suitable manner and according as may be desired. The rocker shaft or stud 105 may be provided with the crank arm 112 which issecured thereto to rotatethe same and which crank arm pivotally connects with the lifting rod 113, as shownin F i 1. Said lifting rod is-adjustably couple to the arm 114 of the worklngbeam 115, the arm 116 of which is pivotally coupled through the connecting rod 118 with the sliding block 119 of the actuating mechanism, as for example, the Stephenson link valve ear mechanism 120 shown in said Fi 1, w ich is actuated by the ahead an reverse eccentric rods 121-and 122,respectively,engagin with eccentrics (not shown) provided on t e engine crank shaft for the urpose. Said link mechanism 120 is coup ed with andcontrolled by the operating lever 123 in the usual manner for link adjustment and shift-- ing purposes, and which operating lever 123 preferably works about the usually attendfixed and notched are 124. The full line position of-said lever 123 shown in Fig. 1, represents the full ahead position of the valve gear; the dotted position marked N represents the neutral position thereof when the engine is at rest; and the ;-;dotted position marked R represents the 'full reverse position of the link motion when the engine is in full reverse.

Referring .to the diagrammatic views 13 to 15 inclusive, the parts are similarly numbered to correspond to the parts of the mechanism already described. The letter P represents the feed pump in the oil supply system which is provided with the regulable by-pass valve T for regulably throttling the by-passing of the pump to.var the pressure at which the oil is being elivered to the supply pipe 41. 'X, X and X. represent distinct angular settings of the plunger arm 109 which correspond to the angular settings Y, Y and Y of the displacement plunger arm 108. In Fig. 16 the rectangular boxes indicate corresponding areas displaced by the displacement and pressure plungers of the apparatus between the relashown in Figs. 13 to 15 inclusive.

Having thus described the parts of my inventionin detail, the manner in which the same may be operated is as follows:

First, it must be noted that while the drawings, as per Fi 1, show the apparatus coupled with the or inary ty e of valve gear known as the Stephenson link motion, for

actuating and regulably'cont-rolling same,

the apparatus, if desired, may be coupled with a-shaft governor mechanism insteadfor providing automatic regulation and will function therewith to equal advantage.

Secondly, it will be noted that while the mechanical functioning of the apparatus is primarily controlled through the actuations imparted thereto, through said governor or link motion mechanisms, the a paratus possesses features in the design t ereof-which permit of further mechanical regulation, as for exam Ie, the discharge or in'ecting valve-lift imiting-screw 103, the ad usting spring 98, the regulable connection of the pressure plunger arm 109, the adjusting stem 51, and the adjustable working beam 1 arm 114.

Thirdly, that the apparatus may be employed with any of the various fuel oils employed in internal combustion engines, particularl with the heavier and less expensive oi s, that the pressure of the oil delivered to the apparatus may be regulated to thedesired pressure by means of throttling a by-pass pipe em loyed in connection with the pump mec anism P, as suggested and indicated in Fig. 13.

'Fourthly, that the cut-off valve 45 is designed to provide a differential valve which is actuated by the difference of pressures existing between the oil from the supply to thel apparatus and the oil acted upon within, the apparatus, the area of the valve exposed to the former pressure being relatively large while, the area of the valve exposed to the latter pressure is relatively smaller, as may be noted from an examination of the structure of said valve shown in the enlarged views in Figs. 6 and 7. The function of said cut-ofi valve is to by-pass the oil from within the ap aratus back therethrough to the supply when the pres: sure on said oil within the apparatus goes beyond a predetermined pressure, thereby cutting oil the discharge through the. discharge or injecting valve ofthe apparatus independent and regardless of the longer discharge range supplied to the apparatus by the actuating governor or link motion mechanisms.

Fifthly, that the design of the discharge or injecting .valve mechanism of the apparatus provides a compression reservoir for the oil delivered thereto, which is of an appreciable volume and is directly exposed to the heat of the combustion chamber of the engine cylinder, whereby the oil contained in said reservoir is thus preheated before being discharged from the valve, and that the orifice provided between the discharge valve seat and the lift of the valve when open is only sufficient to allow for a thin film of oil to be forced through, which oil between the preheating and pressure actions to which the, same. is subjected within the device, is thoroughly pulverized and conditioned to become gasified upon leaving the valve seat and entering the engine cylinder.

Sixthly, that the control of the pulverizing feature'of the apparatus is available to any desired extent to yield the necessary and required pressure to properly pulverize any given quality of oil, so that its tendenc to burn is consistent and commensurate wit the turning period of the engine;

Se'venthly, that the discharge or injecting valve of the, apparatus is subjected to the compression pressure of the engine cylinder, which pressure increases the tendency of the valve to lead according to load and depending-on the s eed of the engine; thus having the efi'ect o offsetting the lag in the valve at high speeds.

Eighthly, that the combined action of the co-operating displacement and ressure plungers of the apparatus is directe to put pressure on the oil chamber in the valve mechanism thereof and does not deliver or pump the oil; the pumping action thereof,

however, serves to augment the delivery action of the supply pump at the time of delivery to the valve mechanism of the apparatus.

Ninthly, that the apparatus employs an auxiliary valve ear or link mechanism therewith which uplicates the functioning properties of a cam and which is itself variably actuated by the variable reciprocations imparted thereto through the actuating shaft governor or shaft driven link motion mechanisms and Finally, that the peculiar construction of the ap aratus confines the high pressure zone wit the apparatus proper and thus overcomes and eliminates the usual objectionable feature of transmitting high pressure oil through a pipe line which offers mechanical disadvantages and which has been proven troublesome and unreliable.

The apparatus assembled with an engine, as indicated in the drawings, operates in the following manner: The reciprocating action of the actuating shaft-controlled governor or link motion mechanisms serving as the primary operating gear imparts a reciprocating action to the lifting rod 113, which oscillatingly carries the crank arm 112 and consequently oscillates the bellcrank 107. The maximum throw ofsaid bellcrank attending either the full ahead or full reverse setting of the linkmotion or governor mechanism is between the points Y "and X X 'Ior'the 'displacement and pressure plunger arms 108 and 109, respectively, as shown in Figs. 1, 13, 14 and 15. Hence any intermediate setting of the actuating mechanism, as between the neutral position N and the full ahead or full reverse positions of the lever 123, will correspondingly reduce the throw of said bell-crank between the aforesaid limiting points Y -Y and X p The maximum throw Y-Y of the displacement arm 108 in respect to the operating center line Z- Z (Figs. 1, 13 to 15 inclusive) yields two strokes to the displacement plunger 72; that is to say, from Y to Y the displacement plunger .72, as shown in Fig.

13, recedes the distance S and from Y 1 the direction of travel of the displacement lunger is reversed and the travel thereof 1s eqpal to S. Hence two strokes are made e dis lacement plunger which are each equal to S and oppositely disposed between the points Y* 1 or Y On the other hand, the arc of travel of the pressure plunger arm 109 is entirely to one side of said operating center line Z-Z; and therefore, while the displacement arm moves from Y to Y and yields two reciprocating strokes on the displacement plun er 72, the pressure plunger arm, during t e same interval, yields but a single stroke, which as shown in Fig. 13, is equal to 28. The latter figure represents the setting of the delivery stroke mechanism of the auxiliary valve gear, namely, the bell-crank. 107, operating the displacement and pressure plungers 72 and 73 respectively. Said delivery stroke at the beginning thereof positions the displacement and pressure plungers in the Y and X positions, respectively, as there shown, and which plungers during the delivery stroke function as follows: From Y to Y the plunger 72 moves the distance S in the direction of the arrow marked a. During said. period the pressure plunger 73 moved in the opposite direction a distance also equal to S, when the setting of the auxiliary valve ear assumes the position shown in F ig. 14.

he effect of that portion of the delivery stroke is that the displacement plunger moving the same distance as the pressure plunger, but opposite thereto when the areas of the plungers are equal, neutralizes the effect of the pressure plunger and renders that with the pressure plunger and in the same.

direction therewith, when it will be understood that the full force of both plungers is directed against the oil in the apparatus and thus that portion of the delivery stroke becomes the effective portion of the stroke. Similarly, when the auxiliary valve gear is actuated between the points Y to Y and X to X the intake stroke of the plunger is effected in this case; both plungers move out together from Y to Y and X to X which permits the .charging with oil of each plunger bore with an amount equal to S; then as the gear continues on said intake stroke, from Y to Y and X to X the displacement plunger72 reverses its direction of travel and travels the distance S which is equal to the distance S which the pressure plunger 73 continues to make but in its original direction which is now op osed to the direction assumed by the dispfiicement plunger. Hence, the two plungers during this second half ofthe intake stroke neutralize each other and render an ineffective and neutral: result or stroke.

The diagram shown in Fig. 16 schematically shows the comparative sequence of operations between the co-operating dis-v placement and pressure plungers, where it will be noted that the first half of the inlet stroke is effective (both plungers moving in the same direction as indicated by the arrows), the second half of said stroke is neutral (plungers opposed to each other), the first half of the delivery stroke is neutral (plungers opposed to each other), and finall the second half of the delivery stroke is e ective (both plungers moving in the same direction).

It will here be noted that I have shown the plungers as havi-n equal diameters, hence equal lengths 0 stroke will yield equal displacing volumes. It v ill, however, be understood that plungers of unequal areas may be employed, but the relationship of length of stroke would have to be correspondingly varied to provide the feature of equal volume displacement for effecting the hereinabove neutralizing feature of said plungers.

The resultant action of the auxiliary valve gear, as affectin the co-operating oil plungers of the within apparatus, duplicates the functions of a cam and makes such a cam action available through the actuations of a reciprocating mechanism, as the aforementioned shaft controlled governor or valve gear link motion mechanism, either of which may serve as the primary controlling and actuating medium for the auxiliary or secondary valve gear effecting the aforesaid cam action.

Intermediate settings of the primary actuating mediums, as for example, between the neutral position N and the full ahead or full reverse positions of the operating lever 123, will proportionately reduce the length of stroke S of the oil plungers and will correspondingly reduce the pressure effect on the oil in the apparatus, the stroke S being the maximum length of stroke obtainable for the maximum setting of full ahead or reverse positions of the primary actuating valve gear and corresponding to full load.

The cut-off valve 45 of the apparatus is designed to be automatically operated by the difference of pressures acting lhcreagainst; the same being designed with a relatively high differential of say 60 to 1 for example; that is to say, the area exposed to the supply duct 40 is sixty times that of the area exposed to the duct 54 and in which'the oil pressure is raised by the action of the above described co-operating oil plungers to a very high pressure. Said cut-off valve is normally spring-seated by the load spring 53 which is regulable and adjustable. Thus, on a 60 to 1 differential, if the oil supplied within the apparatus, which is delivered thereto by the pump P- through the supplypipe 41, is 100 lbs. per square inch, the pressure in the apparatus on theoil subjected to the action of the oil plungers would have to be built up to at least 6000 lbs. per square inch before the pressure in the duct 54 would unseat said cut-off valve and permit the oil to by-pass back to the supply through the vent holes 48 provided for the purpose. Obviously by varying the pressure of the oil supplied to the apparatus, which may be accomplished by throttling the by-pass valve T of the pump P (Fig. 13) the relative building up pressure of the apparatus will be accordingly affected.

The fuel oil is thus forced into the apparatus under the desired pressure through the supply duct 40, which oil passes the ball checks 63 and 58 initially filling up the upper bore 42, the bore within the sleeve 55, the cut-off valve duct 54, the ducts 44, 85, 83, 84,

39, 38 and the annular oil reservoir 87 at the bottom of the delivery or injecting valve mechanism formed between the collar 82 and the valve plunger 90 (Fig. 3), all of which form the hi h pressure chamber of the apparatus. Su sequent to the initial charging of said high pressure chamber, the supply pumps only admit the quantity of oil displaced by the discharge from said high pressure chamber per engine stroke for relling said high pressure chamber.

The effective delivery stroke of the co= operating displacement and pressure plungers of the apparatus acting against the noncompressible oil charged within said hi h pressure chamber rapidly builds up t e pressure of the oil therein and hydraulically forces the valve to unseat a ainst the pressure of the load spring 98 and discharges the oil under high pressure within the engine cylinder. Said oil within the high pressure chamber of theapparatus being preheated by the heat of compression and combustion of the engine cylinder together with the high pressure directed thereagainst leaves the valve seat thoroughly pulverized and in the form of a gas susceptible of immediate ignition and in a steady stream equal to the range allowed by the particular setting of the primary valve gear unless otherwise aflected by the automatic cut-elf valve which would foreshorten the normal range of delivery provided by said primary operating gear. Hence, the rate and range ofdeliv'eryof the oil from the discharge or injecting valve of the apparatus may be re lated to suit any requirement of the engine y changing the pressure of the supply oil or by manipulating the primary valve actuating mechanism, or both; further regulation being effected by the adjustment of the load spring 98 and by the setting of the limiting stud 103, as may be understood.

The apparatus is thus possessed of features which render the same absolutely flexible and positive in its operations. The mechanism emplo ed is exceedinglyv sim le and may be regu ated to handle any gra e of oil.

While the gear setting provides a definite delivery range for the apparatus, it will be understood that by varying the pressure of the supply system, thecut-od valve may be put into action to provide any foreshortened cut-oil to the dehvery range that may be desirable. Also, that the delivery valve 90 being directly subjected to the compression pressure of the engine cylinder will yield an automatic lead for the valve commensurate with the running requirements of the engine. Further, the high pressure oil chamber may be designed to provide a reservoir of oil which is many times in excess of the quantity actually desired to be discharged through the a paratus per engine stroke and which oil w en subjected to the eraavr heat of compression and combustion is pre heated before being discharged, which results in the complete pulverization of the oil.

In the theoretical diagrams shown in Figs. 10 to 12 inclusive, the functioning cycle of the within apparatus is graphically represented. The outer and inner circles DP and PP represent the measure of movement of the co-operating oil plungers '4' 2 and 73 of the apparatus on the delivery (discharge) or pressure stroke which is equal to S. 2S equals the stroke of the pressure plunger 73. The displacement plunger 72 makes two strokes to each stroke of the pressure plunger 73. The displacement plunger 72 moves from the outer circle DP to the inner circle PP when the pressure-plunger 73 moves from the 4 position to the 0 position or PP circle, and

from the O or PP circle to the full stroke both plungers move out together.

L represents the lead given the discharge valve of the apparatus, which may be variably and regulably controlled by adjustment of the prime? valve gear mechanism of the apparatus. he upper portion of the diagram Fig. 10 above the line Y-"-Y represents the discharge function of the apparatus, while the lower portion represents the inlet function thereof. Thus the. quadrant XAY represents the effective range or portion of the delivery or discharge stroke of the apparatus, the quadrant YDX the effective portion of the inlet stroke, the quadrant KEY the neutral portion of the inlet stroke, and the quadrant YXX the neutral portion of the delivery or discharge stroke of the apparatus (compare with Fig. 16). The edective delivery stroke of the apparatus, as may be understood from the mechanical functions of the valve gear employed with the apparatus, is variable according to the setting of the primary operating element, namely, in the embodiment shown in the drawing the Stephenson link. Niiturally, from the neutral position N, as indicated by the operating lever 123 in Fig. 1, to the full ahead position indicated by the full line position of the lever 123, the stroke of the co-operating displacement and pressure plungers is varied and represented in Fig. 10 by the different positions numbered from 0 to 4 inclusive. 0 represents the neutral setting or N position of the lever 123 when no stroke is provided to the displacement and pressure plungers; and 4 represents the correspondingly decrease said maximum range of delivery and foreshorten the same, as indicated in Figs. 11 and 12. Also, that by regulating the pressure ofthe oil delivered to the apparatus (that is, by increasing said pressure of said oil supply) any range of delivery otherwise available by the specific setting of the primary actuating mechanism, may be foreshortened to yield an earlier cut-off, as Figs. 11 and 12 represent.

The within apparatus thus provides an exceedingly simple device which is applicable to all classes of internal combustion engines, operating on the fuel injection principle, and because of its range and scope as to handling the various grades of fuel oils, its certainty and reliability of operation, its flexibility and its effective character supplies along-felt want in the art.

While the preferred embodiments of my invention have been described in detail, it will be understood that I do not wish to be limited to the particular construction set forth, since various changes in the form, material, proportions, arrangement of parts, and in the details of construction may be resorted to without departing from the spirit and scope of the invention, or destroying any of the advantages contained in the same, heretofore described and defined in the subjoined claims.

Havin thus described my invention in detail, w at I claim as new is:

1. An apparatus for delivering liquids.

comprising a preliminary low pressure system, a high pressure system, said low pressure system being in constant communica tion with said high pressure system, means for maintaining a fixed ratio between said systems and an ejector valve for controlling the delivery of the liquid.

2. An apparatus for delivering liquids comprising a system including, means for putting the liquid under preliminary pres sure, a second system including means for raising the pressure of the liquid to a higher pressure than, and controlled by theprelnninary pressure and an ejector valve adapted to restrain the delivery of any liquid having a pressure less than a predetermined minimum.

3. An apparatus for delivering liquids comprising, a system including means for putting the liquid under preliminary pressure, automatic means adapted to maintain said preliminary pressure constant, a second system including means for raising the pressure of a portion of the liquid to a higher pressure automatic means adapted to maintain a constant predetermined ratio between the high and low pressure of the liquid and means adapted to measure and deliver the quantity of liquid at the higher pressure.

4. An apparatus for delivering liquids comprising a system including, means for putting the liquid under preliminary pressure, a second system including means for raising the liquid to higher pressure, having a fixed ratio to the preliminary pressure, a valve adapted to automatically maintain the ratio between the preliminary and the higher pressures, and an ejector valve.

5. An apparatus for delivering liquids com rising a system including, means for putting the liquid under preliminary pressure, manually adjustable automatic means for predetermining said pressure and a second system including means for raising the pressure of the liquid higher than, but

limited by, the preliminary pressure and an ejector valve adapted to restrain the delivery of the liquid until its pressure has reached a predetermined minimum.

6. An apparatus for delivering liquids comprising a system including means for putting the liquid under preliminary pressure, a second system including means for raising the pressure of the liquid to a higher pressure having a fixed ratio to the prelimi nary pressure and means controlling the higher pressure adapted to measure the quantity of the liquid delivered.

7. An apparatus for delivering liquids comprising a system including, means for putting the liquid under preliminary pressure, a second system including means for raising the pressure periodically to a higher pressure, having a fixed ratio to the preliminary pressure, means adapted to measure the quantity of liquid and means adapted to modify the quantity of liquid measured for delivery.

8. An apparatus for delivering llquids comprising a system including means for puttlng the liquid under preliminary pressure, a second system including means for raising the pressure of the liquid to a higher pressure bearing a fixed ratio to the preliminary pressure and adapted to measure the quantity of liquid by its stroke and means for changing its effective stroke.

9. An apparatus for delivering liquids comprising a system including, means for putting the liquid under preliminary pressure, a second system including means for raising a portion of the liquid to a higher pressure and adjustablymeasuring; and delivering any desired-quantity of fluid at the higher pressure and means adapted to automatically maintain a constant predetermined g ratio between the preliminary and the high pressure.

10. The herein described method of delivering liquids which consists in subjecting the liquid to a predetermined preliminary pressure, then subjecting a portion of the liquid to a higher pressure, delivering the li uid and controlling the quantity of liquid de ivered b the preliminary pressure.

11. The herein described method of delivering liquids which consists in subjecting the liquid to a'predeterimned preliminary pressure, automatically maintaining said preliminary pressure, then subjecting the liquid to a higher pressure, automatically limiting said higher pressure, delivering the liquid and controlling by the first-named pressure, the quantity of liquid delivered.

12. The herein described method of delivering liquids which consists in subjecting the liquid to a predetermined preliminary pressure, then subjecting the liquid to a higher pressure, the higher pressure having a fixed ratio to the preliminary pressure, delivering the' liquid and controlling by the first-named pressure the quantity of liquid delivered,

livering liquids which consists in subjecting the liquid to a predetermined preliminary pressure, then subjecting the liquid to a higher pressure, delivering the liquid and controlling automatically by the first named pressure, the quantity of liquid delivered.

14. The herein described method of delivering liquids which consists in subjecting the liquid to a variable preliminary pressure, then subjecting a portion of the liquid to a pressure having a fixed ratio to the preliminary pressure, then delivering the liquid against a resistance restraining the flow of same at all pressures below a predetermined minimum.

15. The herein described method of delivering liquids which consists in subjecting the liquid to a variable preliminary pressure, then subjecting a portion of the liquid to a higher pressure,'having a fixed ratioto the preliminary pressure; measuring the given quantity of liquid, then delivering the liquid against a resistance restraining the flow of same at all pressures below a predetermined minimum,

In testimony whereof, I hereto aflix my signature, this eleventh day of April, 1921'.

WILLIAM B. SMITH WHALEY. 

